Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
  • F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
  • F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
  • F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
  • F04B9/103—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber
  • F04B9/107—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having only one pumping chamber rectilinear movement of the pumping member in the working direction being obtained by a single-acting liquid motor, e.g. actuated in the other direction by gravity or a spring

Definitions

• HYDRAULIC MACHINE ESPECIALLY A HYDRAULIC ENGINE, AND A DOSER COMPRISING SUCH AN ENGINE.
• the invention relates to a hydraulic machine, in particular a hydraulic motor, of the type that includes:
• an envelope comprising a body and a lid
• separating means adapted to perform reciprocating movement in the envelope between body and lid, the separating means defining two chambers; - Hydraulic switching means for the supply of liquid and the evacuation of the chambers, these switching means comprising a dispensing member which can take two stable positions and controlled by the movements of the separating means;
• Hydraulic machines of this type especially the proportional proportional hydraulic motors, operate for the most part with a distribution system of the "valve box" type.
• the valve box is a fluid distribution system consisting of an inlet and outlet valve per working chamber, the valves being provided with seals.
• the object of the invention is, above all, to provide a hydraulic machine, in particular a hydraulic motor, whose switching means make it possible to separate the distribution mechanism from the driving part, so that the disassembly of these elements can be done independently. one of the other.
• a hydraulic machine in particular a hydraulic motor, of the kind defined above is characterized in that the dispensing member comprises a dispensing spool pressed against a fixed flat plate relative to the body of the casing, the dispensing spool. being able to slide sealingly, seamlessly, against the plate which has orifices connected respectively to the chambers of the casing and to an outlet orifice of the liquid, the dispensing spool being provided for, depending on its position, closing some of the orifices or put them in communication with the arrival of fluid or the exhaust.
• the elastic means is advantageously constituted by a curved arc-shaped spring, one end of which is connected to a link articulated on an axis carried by the body of the casing, one end of the link being connected to the pusher, while the other end of the spring is linked in translation to the slide, this other end passing from a stable position to another stable position by deformation of the spring.
• the link is secured to at least one arm bearing against a stopper of the slide at the time of the reversal of the direction of movement to assist the spring force at the beginning of the movement of the slide.
• the end of the curved arc-shaped spring connected to the pusher passes, during the movement of the pusher, from one side to the other of the axis of articulation of the rod.
• the end of the curved arc spring connected to the drawer can be received in an elongated housing in the direction of movement of the drawer.
• the spring is advantageously made of plastic, and hinge pins provided at each end are molded in one piece with this spring.
• the flat plate preferably comprises five orifices spaced in the slide sliding direction, namely a central orifice connected to the outlet of the hydraulic machine and, on either side of the central orifice, two spaced apart orifices connected to each other.
• one chamber of the machine, the drawer having at its longitudinal ends means for closing a hole of the plate and, between its ends, a communication space between at least two holes of the plate.
• the spacing between the central orifice and an orifice adjacent to the plate is less than the spacing between this adjacent orifice and the end orifice located on the same side, the communication space of the slide ensuring, during the reversal of the direction of movement of the separation means, placing the two chambers in communication with the outlet, and therefore the inlet with the outlet.
• Each closure means of the dispensing spool comprises a closure zone delimited by two walls transverse to the direction of displacement, suitable for closing an orifice of the plate when it is at the right of this orifice, and the space of communication of the dispensing spool, between the closure zones, is limited by a wall spaced from the plate.
• the dispensing spool and the flat plate may be arranged parallel to the direction of movement of the pusher.
• the surface of the flat plate in contact with the drawer is an ice.
• the flat plate may be ceramic.
• the drawer can be made of plastic.
• the separation means is advantageously a membrane.
• the invention also relates to a proportional proportioner of an additive in a main liquid, characterized in that it comprises a hydraulic motor as defined above and a metering subassembly of the additive actuated by the engine.
• the dispenser may include a separating plug provided in the bottom of the compartment containing the switching means, this plug being traversed by a. piston of the dosing subassembly connected to the pusher, and a pipe opening under the plug and connected to the outlet.
• the invention consists, apart from the arrangements set out above, in a certain number of other arrangements which will be more explicitly discussed below with reference to an embodiment described with reference to the accompanying drawings, but which is in no way limiting.
• 1 is a schematic vertical section of a proportional proportioner with hydraulic motor according to the invention.
• Fig. 2 is an exploded perspective view of the main parts of the metering unit and the hydraulic motor.
• Fig. 3 is a diagram illustrating a first extreme position of the mirror and the drawer folded on the side for ease of explanation.
• Fig. 4 shows, similarly to FIG. 3, the ice and the drawer in an intermediate position.
• Fig. 5 shows, similarly to FIG. 3, the ice and drawer in another extreme position, opposite that of FIg.3.
• Fig. 6 is a schematic vertical section of the ice and drawer shown horizontally in an extreme position.
• Fig. 7 is an elevational view of the drawer and the link of Fig.6.
• Fig. 8 shows, similarly to FIG. 6, the tilted link.
• Fig. 9 is an elevational view of the link and the slide of FIG. 8.
• Fig. 10 is a schematic section similar to FIG. 8 of the rod and drawer being slid.
• Fig. 11 shows in elevation the drawer and the link in the position of FIG. 10.
• Fig. 12 is a schematic section similar to FIG. 10 of the rod and the slide in the other extreme position for the control of the inversion and the change of direction of the liquid flows, and FIG. 13 shows in elevation the drawer and the link in the position of FIG. 12.
• a proportional proportioner comprising a hydraulic motor 1, for a metered injection of additive into a main liquid which actuates the engine.
• the motor 1 comprises a casing 2 formed of a body 3 and a lid 4.
• the body and the lid are dismountably assembled, by bolts and nuts not shown, passing through holes provided in mating flanges.
• the lid 4 is equipped with a purge Am to evacuate the air from the dispenser.
• the separating means M is advantageously constituted by a deformable membrane 7 whose periphery comprises a bead tightly sealed between the cover 4 and the body 3.
• This embodiment of the separating means M is not limiting, the invention being applicable to a machine whose means of separation is constituted by a piston.
• the central portion of the membrane 7 has a circular opening whose edge is tightly sealed between a disk 9 housed essentially in the chamber 6 and a ring 10 housed in the chamber 5.
• the ring 10 can bear, at the end of high stroke of the membrane 7, against a rib 1 1 of the inner surface 8.
• the chamber 6 is delimited, on the opposite side to the membrane 7, by a cylindrical cavity whose bottom 12 comprises a passage for a pusher A.
• Hydraulic switching means C are provided for the supply of liquid and the evacuation of the chambers 5 and 6. These switching means C comprise a distribution member D that can assume two stable positions and are controlled by the displacements of the membrane 7.
• the switching means C are housed in a compartment 13 of the body 3 of the envelope, connected to an inlet 14 of liquid under pressure.
• Trigger means 15, comprising the pusher A connected to the membrane 7, are able to cause a high end and a low end of a sudden change in the position of the switching means C under the action of an elastic means B, for the reversal of the stroke of the membrane 7.
• the dispensing member D comprises a dispensing spool 16 applied against a flat plate 17 fixed relative to the body 3 of the envelope.
• the plate 17 is constituted by an ice, that is to say that the surface of the plate 17 in contact with the distribution slide 16 has a high degree of flatness corresponding to a mirror polish.
• the combined surface of the slide 16 also has a high degree of flatness so that a seal without contact is established between the glass 17 and the drawer 16.
• the plate 17 is advantageously made of ceramic while the drawer 16 is made of plastic material.
• the plate 17 comprises, for the passage of the liquid, five orifices spaced in the direction of sliding of the slide 16, the vertical direction according to the example of FIG.
• the plate 17 and the slide 16 are arranged parallel to the direction of movement of the pusher A and orthogonal to the geometric axis of the inlet 14.
• the slide 16 can slide against the plate 17 parallel to the direction of movement of the pusher A.
• the plate 17 has a central orifice S connected to the outlet 18 of the hydraulic machine and, on either side of the central orifice in the direction of movement of the slide, two spaced orifices E5, P5 and E6, P6 connected by pipes provided in a part 19 fixed against the body 3 of the machine.
• the piece 19 is itself connected by two elbows 20 (FIG 2) to the upper chamber 5.
• the connections with the lower chamber 6 are shown only partially.
• the lower part of the compartment 13 is open and receives a metering subassembly 21 with suction valve provided with a nozzle 23 to which a duct may be connected in a container (not shown) of additive sucked in metered quantity.
• the metering subassembly 21 comprises a suction piston 24 hooked to the pusher A.
• the piston 24 passes through a separating plug 25 provided in the bottom of the compartment 13.
• the additive liquid pumped by the piston 24 is discharged towards the outlet 18 through a pipe 26 which opens below the cap 25.
• the mixture of the additive, pumped by the subset 21, with the main liquid arriving through the inlet 14 is made at the outlet 18.
• the mixture of the additive and the main liquid could take place in the compartment 13 by removing the plug 25 and closing the pipe 26.
• the plate 17 is housed in a recess 27 provided in a plastic block 28 having holes 29 for attachment to the piece 19, and stops 30, 31 end of travel of the drawer 16.
• the distance between the central orifice S of the plate 17 and a neighbor orifice E5 or E6 is less than the spacing between this orifice E5 or E6 and the extreme orifice P5 or P6 situated on the same side.
• the pitch between the orifices is offset, which is of interest explained below.
• the drawer 16 has at each of its longitudinal ends a closure means comprising a closure zone 32, 33 of an orifice of the plate 17 and, between the closure zones, a communication space 34 between at least two holes in the plate 17.
• Each closure zone 32, 33 of the slide 16 is delimited by two walls transverse to the direction of movement, providing a virtually linear contact with the plate 17, favorable to the establishment of a good seal. Between the transverse walls bearing against the plate 17, the wall of the closing zones 32, 33 is parallel to the plate 17 and spaced from its surface.
• the communication space 34 located between the closing zones 32, 33 is limited by a dome-shaped wall 35.
• the resilient means B is constituted by a spring 36 with a curved arc-shaped blade whose convexity is turned towards the upper part of the body 3. One end 36a of the spring is connected to the pusher A while the other end 36b is translationally connected to the slide 16.
• Each end 36a, 36b is advantageously formed by a cylindrical pin whose generatrices are orthogonal to the mean plane of the leaf spring 36, and to the direction of movement of the pusher A, these cylindrical pins forming a pin joint.
• the spring 36 is preferably made of plastic in one piece with the pins 36a, 36b.
• the pins of the ends 36a, 36b protrude transversely on either side of the leaf spring 36 along its width.
• the lateral projections of the end 36a are received in respective housings provided at one end of two parallel branches of a rod 37, these branches flanking the spring 36.
• Each housing receiving the end 36a is open so that the end 36a can be engaged and easily released from the housing of the rod 37 by simple deformation of the spring 36.
• the rod 37 is articulated, at its end remote from 36a, on an axis 38 supported, at each of its ends, by a member 39 (Fig.2) substantially in the shape of an isosceles triangle, with inner opening, whose base is integral. of the piece 19 and the body 3, and whose top area comprises a bearing for the end of the axis 38.
• the two supports 39 frame the drawer 16 and the link 37.
• each leg of the rod 37 opposite the axis 38 and which is connected to the end 36a of the spring 36 comprises a cheek 40 in which is provided the housing for the end 36a.
• Each cheek 40 has a substantially circular shape and is housed, with the possibility of rotation, in a groove 41 horizontal.
• Each groove 41 is provided in an inner vertical wall of a rectangular window 42 formed in the portion of the pusher A in the compartment 13.
• Each groove 41 opens, on the side of the plate 17, by a flared portion allowing a tilting of the rod as shown in Fig.1.
• This arrangement allows, during the drive in translation by the pusher A cheeks 40, a rotation of the rod 37 about the axis 38.
• the other end 36b of the spring 36 is received in a rectangular housing 43, elongated next the direction of movement of the slide 16.
• a housing 43 is provided in each of two side walls 44 of the slide 16, which frame the spring 36.
• the housing 43 is open in the opposite direction to the plate 17 and the spring force 36 applies the end 36b against the bottom of the housing 43.
• the establishment of the pin constituting the end 36b in the housing 43 is simple and fast, as well as disassembly.
• the end 36b can occupy a stable position shown in Fig.1 and Fig.12 where it abuts against the transverse wall of the housing 43 furthest from the chamber 6.
• the drawer 16 then occupies the lower position illustrated in FIG. 1.
• the end 36b of the spring bears against the transverse wall of the housing 43 closest to the chamber 6, and the slide 16 occupies the high position opposite to that of FIG. .
• the end 36a of the spring connected to the pusher A by the link 37 passes, during the vertical movement of the pusher, from one side to the other of the hinge axis 38 of the rod 37.
• This passage causes the triggering of switching and changing the position of the drawer
• the rod 37 is integral with at least one arm 45 substantially orthogonal to the rod and extending on either side of this rod as shown in FIGS. 6 to 13.
• the arm 45 is in the form of a balance wheel of which the ends 45a, 45b are bent and rounded to come into contact, at the moment of reversal of the movement of the membrane, with a stop 46, for example in the form of a prism, provided projecting on the outer face of the side wall 44 of the drawer, at mid-length, below the rectangular housing 43.
• the drawer 16 has been shown folded so that, in fact, it slides against the plate 17 in a position orthogonal to that shown in these figures.
• the width of the spool 16 is greater than that of the orifices of the plate 17 so that when an orifice is covered by one of the end closure areas 32 or 33 of the spool, this orifice is completely closed.
• Fig. 3 represents a first stable end position of the slide 16 in which the closing zone 32 closes the orifice E5 connected to the chamber 5, while the closing zone 33 closes the orifice P6 connected to the chamber 6.
• the intermediate space 34 communicates the orifice E6, and therefore the chamber 6, with the fluid outlet S.
• the orifice P5 of the plate 17 is open and receives the pressurized liquid which arrives in the compartment 13 and is directed towards the chamber 5.
• Fig. 4 represents an intermediate position of the drawer 16 in which the sealing areas 32, 33 are in line with the separation zones between the two orifices located on either side of the central orifice S of the plate 17.
• the orifices P5 and P6 communicate with the compartment 13 so that the pressure is admitted into both the chamber 5 and the chamber 6.
• the space 34 communicates the two exhaust ports E5, E6 with the outlet port S In this intermediate position the five orifices are in total communication and are all open at full section.
• the flow of liquid passes through the chambers 5 and 6 and the pressures equilibrate on both sides of the membrane 7.
• FIG. 5 represents the other extreme stable position of the slide 16 according to which the orifice P6 is open and receives the pressurized fluid which is directed towards the chamber 6.
• the orifices E6 and P5 are closed by the slide 16, while the port E5 is connected to the output S.
• the pitch offset on the one hand between the outlet orifice S and the orifices E5, E6 and, on the other hand, between these orifices E5, E6 and the orifices P5, P6 makes it possible to never put in communication, in extreme position stable drawer 16, the inlet pressure with the outlet chamber, while in the intermediate position of FIG. 4 all the orifices are in unrestricted communication to reduce the pressure on either side of the membrane 7.
• the membrane 7 has reached the end of the low stroke and the link 37 has tilted, under the action of the spring 36, which has moved the distribution spool 16 into the high stable position bearing against the abutment 30.
• the pressurized water arriving through the inlet 14 is admitted through the opening P6 open in the lower chamber 6.
• the other orifice E6 communicating with this chamber 6 is closed, while the orifice E5 is connected to the outlet 18.
• the pressure exerted in the chamber 6 on the membrane 7 causes the deformation of this membrane to the chamber 5 and the displacement of the pusher A upwards according to Fig.1.
• the liquid of the chamber 5 is discharged through the orifice E5.
• the end 36b of the spring 36 remains in abutment against the upper transverse wall of the housing 43 and holds the slide 16 in this position.
• the rise of the pusher A causes the end 36a of the spring 36 to rise.
• the end 36a crosses upwards, according to FIG. 1, the horizontal plane passing through the axis 38 of articulation of the link 37, the latter flips relative to the pusher A so that the end 36a passes above the axis 38 when looking Fig.1.
• FIG. 10 and 11 represent the relative position of the rod 37 and the drawer 16 at the end of the assistance provided by the arms 45.
• the drawer 16 having begun its race, the efforts to develop to continue its race are less.
• the spring 36 can thus finish moving the drawer 16 towards the other stable position and the stop 46 deviates from the end 45b as illustrated in Fig.12 and 13 which correspond to the upper end of stroke of the pusher A, shown in Fig.l
• the vertical reciprocating movement of the membrane 7 and the pusher A allows the pumping and dosing of the additive through the metering subassembly 21 whose pumping piston 24 is driven by the membrane 7.
• the drawer 16 is held in place against the mirror 17 by the spring 36.
• the drawer is pressed against the ice 17 by the pressure difference and the liquid inlet flow when there is liquid flow.
• the flatness and surface finish of the drawer 16 and the window 17 ensure a good seal between the two elements.
• the slide 16 is subjected to a normal force to the ice 17 equal to the bearing surface multiplied by the pressure difference.
• the force to move the spool 16 is a transverse force which is equal to the normal force on the spool 16 multiplied by the coefficient of friction between the spool 16 and the spool 17.
• the movement of the diaphragm 7 is mechanically connected and synchronized with triggering the switching.
• the movement of the distribution slide 16 on the window 17 is generated by the rotational movement of the compression spring 36 which "balances" the forces sometimes towards the first stable position, sometimes towards the second stable position, thereby causing the slide 16 to move. by sliding.
• the metering subassembly 21 connected to the membrane 7 via the pusher A, sucks and then directly injects the additive product at the outlet of the metering device.
• the rod 37 driven by the pusher A, provides the compression of the spring 36 and the synchronization of the slide 16. Indeed, under certain limiting conditions (pressure, flow) the spring 36 may not be sufficient to slide the slide 16 on which exerts a pressure difference (pressure at the inlet 14 of the metering unit less pressure at the outlet 18).
• the assistance provided by the rod and the arms 45 is a synchronization that ensures switching under these conditions: the drawer 16 is sufficiently pushed by the arms 45 to the intermediate position, illustrated in FIG. 10 and 11 and in FIG. 4, putting all the chambers of the membrane in communication with the outlet and causing the pressure difference to drop. Efforts on the drawer 16 drop and the spring 36 continues the travel of the drawer 16 to the other stable position causing switching.
• the drawer 16 In the event of a pressure difference and / or a too high flow rate between the inlet and the outlet of the metering device, or in the event of the spring 36 breaking, the drawer 16 is placed by the arms 45 in the intermediate position illustrated in FIG. communication of the two chambers 5,6 with the output, and therefore the input 14 with the output 18.
• the main liquid flow is not interrupted.
• a membrane metering device can have a very low flow rate, for example from 2 to 3 liters / hour. It can operate under a low water pressure corresponding for example to 1 to 2 meters of difference in level between the water source and the doser, about 0.1 to 0.2 bar.
• Such a dispenser makes it possible to pass water laden with particles, in particular thanks to membrane operation.
• the flow range is very wide ranging from 2 - 3 l / h to 2000 l / h for example.
• the operating pressure range is also wide, for example from 0.1 bar to 4 or 5 bar.
• the dosage of additive in the main liquid can be of the order of 2% and even 5%.
• the cubic capacity (flow rate per rise or fall cycle) can be approximately 0.4 liters.
• the diameter of the membrane may be of the order of 110 mm and the stroke of 25 to 30 mm.
• the orifices in the plate 17 may have a section of approximately 1.3 cm 2 .
• the diaphragm dispenser with distribution slide switch makes it possible to separate the distribution mechanism from the piston or diaphragm drive part. As a result, the disassembly of these elements can be done independently of one another.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Reciprocating Pumps (AREA)
• Hydraulic Motors (AREA)
• Multiple-Way Valves (AREA)
• Lubricants (AREA)
• Fluid-Pressure Circuits (AREA)
• Structures Of Non-Positive Displacement Pumps (AREA)
• Coating Apparatus (AREA)

Priority Applications (14)

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ID=36499278

Family Applications (1)

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Cited By (4)

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Citations (4)

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• 2006
  • 2006-01-13 FR FR0600314A patent/FR2896279B1/fr not_active Expired - Fee Related
  • 2006-12-07 BR BRPI0620988A patent/BRPI0620988B1/pt active IP Right Grant
  • 2006-12-07 CA CA2637364A patent/CA2637364C/fr active Active
  • 2006-12-07 PL PL06841881T patent/PL1971776T3/pl unknown
  • 2006-12-07 UA UAA200810357A patent/UA92379C2/ru unknown
  • 2006-12-07 US US12/160,428 patent/US8132497B2/en active Active
  • 2006-12-07 EP EP06841881A patent/EP1971776B1/fr active Active
  • 2006-12-07 DK DK06841881.3T patent/DK1971776T3/da active
  • 2006-12-07 EA EA200870166A patent/EA013486B1/ru not_active IP Right Cessation
  • 2006-12-07 ES ES06841881T patent/ES2342564T3/es active Active
  • 2006-12-07 MX MX2008009064A patent/MX2008009064A/es active IP Right Grant
  • 2006-12-07 AU AU2006334588A patent/AU2006334588B2/en active Active
  • 2006-12-07 CN CN2006800524119A patent/CN101379293B/zh active Active
  • 2006-12-07 AT AT06841881T patent/ATE460585T1/de not_active IP Right Cessation
  • 2006-12-07 JP JP2008549897A patent/JP5289059B2/ja active Active
  • 2006-12-07 DE DE602006012879T patent/DE602006012879D1/de active Active
  • 2006-12-07 NZ NZ569651A patent/NZ569651A/en unknown
  • 2006-12-07 WO PCT/FR2006/002674 patent/WO2007080250A1/fr active Application Filing

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